EP0353856A1 - Turbines - Google Patents

Turbines Download PDF

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Publication number
EP0353856A1
EP0353856A1 EP89306469A EP89306469A EP0353856A1 EP 0353856 A1 EP0353856 A1 EP 0353856A1 EP 89306469 A EP89306469 A EP 89306469A EP 89306469 A EP89306469 A EP 89306469A EP 0353856 A1 EP0353856 A1 EP 0353856A1
Authority
EP
European Patent Office
Prior art keywords
disc
blades
rotor
turbine according
members
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP89306469A
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German (de)
English (en)
Inventor
John Kirby
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0353856A1 publication Critical patent/EP0353856A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/04—Blade-carrying members, e.g. rotors for radial-flow machines or engines
    • F01D5/041—Blade-carrying members, e.g. rotors for radial-flow machines or engines of the Ljungström type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
    • F01D1/06—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines traversed by the working-fluid substantially radially
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T50/00—Aeronautics or air transport
    • Y02T50/60—Efficient propulsion technologies, e.g. for aircraft
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49316—Impeller making
    • Y10T29/4932—Turbomachine making
    • Y10T29/49323—Assembling fluid flow directing devices, e.g., stators, diaphragms, nozzles

Definitions

  • a turbine is, of course, a device for taking power from a working fluid.
  • turbines can also be run as pumps, or compressors, imparting power from an external rotary source to a working fluid
  • the invention also relates to pumps or compressors.
  • Turbine herein, it is to be understood as applying wherever possible to pumps and compressors as well.
  • axial flow turbines typified by the turbines of jet aircraft engines and gas turbine and steam power plants driving large elctric generators.
  • These axial flow turbines comprise a plurality of discs having radially extending peripheral blades.
  • the blades are attached to the discs in a variety of ways, often having specially shaped blade roots which fit into correspondingly shaped slots in the disc periphery.
  • the blades have to be individually fashioned and fitted and the construction is complicated and expensive and, as a matter of commercial practicality, essentially confined to the high performance uses referred to.
  • tangential flow turbine which is in essence like a water wheel in which the working fluid is introduced tangentially to impinge upon vanes at the periphery of a rotary disc member.
  • Either of these types may be a reaction turbine or an impulse turbine, depending on the blade configuration.
  • an impulse turbine the working fluid is directed at a rotary blade with the intention to hit it square-on, so to speak, and impart kinetic energy to the blade through the loss of momentum of the working fluid.
  • the blades are fashioned so as to act more like aerofoil sections and increase the speed of the working fluid over the concave face of the blade as compared to the convex face, whereby to generate "lift" in the tangential direction so as to drive the disc member in rotation.
  • the present invention provides a turbine that is, by contrast, extremely simple and inexpensive to manufacture.
  • the invention comprises a turbine comprising relatively rotatable disc members having an axis of relative rotation and facing each other, each disc having blade members arranged in at least one co-axial ring, the blade members of each disc member extending towards the other disc member and axially overlapping the blade members of the other disc member and the rings being of different diameters whereby the blades of one disc members are closely radially spaced from the blades of the other disc members, there being working fluid inlet and outlet means for working fluid flow in a generally radial direction.
  • One disc member may comprise a stator and the other a rotor.
  • the working fluid inlet means may comprise an inlet central to one of said disc members, and said one of said disc members having central inlet may constitute a stator.
  • the turbine may comprise a disc member having blades on both axially-facing faces. It may comprise two relatively rotatable parts at least one of which has blades on oppositely facing faces. At least one of those parts may comprise bladed disc members disposed axially either side of a bladed disc member of the other part.
  • One part may have a plurality of bladed disc members and another part may then have a plurality of bladed disc members interdigitated with those of the first said part.
  • One of such parts may have disc members connected at outer radius by a casing. Said part may then constitute a rotor, and it may have an outer hoop of high tensile material.
  • the other part may constitute a stator.
  • One of said disc members may be on a shaft, mounted in bearings, the same constituting a rotor.
  • a rotor may comprise an outer ring of blades.
  • the blades may be formed as impulse blades or as reaction blades.
  • the turbine may comprise a disc member having integral blades.
  • the disc member and blades may comprise a casting, or sintered part, or they may comprise a single crystal, for example.
  • Forming the blades integrally with the disc as by casting represents an inexpensive manufacturing method. To improve sealing and reduce leakage it is only necessary to machine axially-facing surfaces of disc and blade tips which in itself is not an expensive procedure. Nor is the provision of annular grooves, which is again a simple machining operation.
  • a bladed disc can be fashioned without multiple independent blade making and fitting operations - the assembly step is cut right out.
  • high temperature materials For turbines required to stand high temperatures, it is desirable to use high temperature materials.
  • high temperature e.g. ceramic or refractory materials are strong in compression but not in tension. Otherwise they are ideal for casting or sintering or otherwise forming into an integral blade/disc unit.
  • Conventional turbine rotors impose tensile stresses on blades and discs alike.
  • single crystal blades have been developed of exotic materials, which are very expensive, however.
  • the bladed rotor discs may be connected at outer radius by a casing and have an outer hoop (as by being tightly wound with high tensile wire or strapping or by the casing being of high tensile material or containing high tensile reinforcement) of high tensile material to counter any tendency to fly apart under centrifugal forces. Substantially all internal forces in the disc are then compressive in nature, in regard to which the blade/disc material is strong. This, of course, can also apply to other kinds of turbine, such as axial flow turbines, and will enable low tensile strength ceramic and refractory materials to be used for the blades thereof.
  • the blades need not be made integral with the discs - they may for example be made separately from the disc members and attached thereto as by welding or, especially with low temperature turbines, by adhesive bonding, or by a mechanical connection, for example, by being lodged in slots or grooves.
  • the invention also comprises a method of making a turbine having a plurality of interdigitated discs with axially extending blades comprising connecting discs in turn alternately axially to build up one and the other of two relatively rotatable members.
  • a stator shaft can be provided with a first stator disc having blades projecting from each face thereof and a rotor assembled around it, one end disc of said rotor being attached to a bearing on the stator shaft and an intermediate disc of said rotor being disposed against the opposite face the said first stator disc to the end rotor disc and attached to the said end rotor disc at outer radius; then another stator disc is brought up to the intermediate rotor disc and attached to the shaft, and rotor and stator discs assembled thus alternatively until a second end rotor disc finishes off the assembly on a second bearing on the shaft.
  • Figures 1 to 10 illustrate turbines comprising relatively rotatable disc members 11, 12 having an axis 13 of relative rotation.
  • one disc member, 11, comprises a stator, the other, 12, a rotor. It will be appreciated, however that although this arrangement is expected to be the usual arrangement, it could also be arranged that both disc members would rotate, whether at different speeds in the same direction, or at different or equal speeds, but in opposite directions, should this be desired for any reason.
  • the disc members 11, 12 face each other and have blade members 14 on the facing faces 11a, 12a of the disc members 11, 12, so that the blade members of one disc member extend from that disc member towards the other.
  • the disc members 11, 12 are so arranged that the blade members 14 of the one axially overlap those of the other.
  • the blade members 14 are arranged in co-axial rings on the disc members 11, 12, the rings being of different diameters whereby the blade members 14 of one disc member are closely radially spaced from those of the other.
  • a working fluid inlet 15 is provided in the centre of the stator disc member 11.
  • a working fluid outlet 16 is provided by the space between the disc members 11, 12 at the periphery thereof.
  • the rotor disc member 12 has a shaft 17 which is mounted in bearings 18.
  • An alternator 19 is shown attached to the shaft 17 as an example of a load to be driven by the turbine.
  • the rotor disc member 12 has an outer ring of blade members 14.
  • the two disc members 11, 12 may be produced as castings, with the blade members 14 cast integrally therewith, thus avoiding the costly separate fabrication and assembly of individual blades of other conventional turbines.
  • the disc members 11, 12 may need to be finished by machining. This may be required on the end faces 14a, or tips, of the blade members 14 and also on the parts 20 of the opposed disc member against which the faces 14a run. Since the faces 14a all lie in a plane, the machining operation on them is carried out in a single milling operation. Since the faces 20 also all lie in a plane, for either of the disc members 11, 12, likewise a single milling operation could achieve the finishing of all these faces simultaneously.
  • separate blade members may be fashioned and welded to the disc members.
  • the blade members 14 illustrated in Figures 1 to 3 are formed essentially as impulse blades.
  • Figure 5 shows a variation in which the blade members 14 are formed as reaction blades with a more pronounced airfoil section.
  • Figure 6 illustrates a blade tip sealing arrangement in which the faces 20 of each of the disc members 11, 12 are recessed below the level of the blade roots 14b in grooves 19a into which fit endwise projections 14c of the blade members 14. This will help reduce leakage of working fluid around the blade tips 14a and improve efficiency. Leakage can be further reduced by attaching annular shrouds 21 ( Figure 7) to the end faces 14a of the blade members 14, the shrouds 21 having lands 21a, and grooves 21b cooperating with grooves 20a and lands 20b of the end faces 20 of the disc members 11, 12.
  • the rotor 12 has a central profiled, essentially conical deflector member 22 ( Figure 4) opposite the working fluid inlet 15 to deflect the working fluid into the radial direction.
  • the disposition of the deflector member 22 may be important in determining the performance of the turbine arrangement, it may project into a nozzle arrangment 22a at the inlet 15 to achieve optimum fluid velocity at the inlet.
  • the arrangement may include a casing or housing 23 ( Figure 4) surrounding the disc members 13, 14 and having an exhaust 24 for spent working fluid.
  • the disc members need not, of course, have plane end faces.
  • Figures 8, 9 and 10 show possible other configurations.
  • the end faces of the disc members 11, 12 are conical, the cone of the rotor 12 fitting with that of the stator 11.
  • Figure 9 shows an arrangement in which the spacing between the opposed end faces of the disc members 11, 12 increases with increasing radius, while Figure 10 shows the opposite.
  • the end faces need not, of course, be conical - they may be surfaces of revolution of curves such as circles, hyperbolae or more complicated curves.
  • the working fluid could be introduced through the exhaust 24 of the housing 23, and exhaust through the inlet 15.
  • the turbine could also, given suitable design, function as a pump or compressor.
  • the turbine can be designed for operation with any desired working fluid such as, for example, steam, compressed air, water or even hot gas as in conventional gas turbines.
  • the number of rings of blades can be anything from one (essentially on the rotor 12) to ten or even more, although the addition of further rings might improve efficiency only marginally.
  • Figure 11 illustrates a multidisc turbine assembly which is capable of operating at higher power than a single disc arrangement for the same diameter.
  • a bearing and seal arrangement 112 carrying an end disc 113 of a rotor 114.
  • the end disc 113 has axially extending blades 115 in concentric rings as described for the preceding drawings.
  • a double-faced stator disc 116 is brought up to it, its blade rings 117A intercalated with the rings of the end rotor disc 113.
  • the stator disc 116 is secured to the stator shaft 111 as by welding.
  • An intermediate rotor disc 118 is now brought up along the stator shaft 111 to the stator disc 116 and located with its blades 119A intercalated with the blades 117B of the double faced disc 116.
  • the disc 118 is secured at outer radius to the disc 113 as by welding or possibly by bolting flanges together.
  • a further stator disc 121 may now be brought up along the shaft 111 to have its blades 122A intercalated with the blades 119B of the rotor disc 118, and secured to the shaft 111.
  • the shaft 111 is closed at one end, open at the other for ingress of working fluid, and has apertures 133 for the working fluid to escape to the working region including the rotor and stator blades.
  • the casing 134 formed by connecting the rotor discs at outer radius is also apertured for the escape of spent working fluid.
  • An outer casing 135 ducts this fluid to an exhaust 136. Power take off is from the hub 137 of the end rotor disc 131.
  • the rotor discs are made of cast or sintered material which is strong in compression but not necessarily so in tension
  • the rotor may be reinforced by rings or hoops of high tensile wire or strip 138. These can be prestressed to counteract centrifugal force whereby the stresses in the rotating discs will all be compressive against the outer rings or hoops 138.
  • refractory materials can be used and especially exotic such materials which can be grown as single crystals, which can be grown in the shape of the rotor or stator disc with integral blades so that even machining can be avoided and certainly assembly of a turbine is made very much easier than when blades have to be assembled to discs.
  • the turbine described and illustrated can be made in various sizes from as small as a few centimetres diameter or less to a metre or more.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
EP89306469A 1988-07-30 1989-06-26 Turbines Withdrawn EP0353856A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB8818208 1988-07-30
GB8818208A GB2221259A (en) 1988-07-30 1988-07-30 Turbines pumps & compressors

Publications (1)

Publication Number Publication Date
EP0353856A1 true EP0353856A1 (fr) 1990-02-07

Family

ID=10641397

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89306469A Withdrawn EP0353856A1 (fr) 1988-07-30 1989-06-26 Turbines

Country Status (6)

Country Link
US (1) US5071312A (fr)
EP (1) EP0353856A1 (fr)
JP (1) JPH0270903A (fr)
DK (1) DK374589A (fr)
GB (1) GB2221259A (fr)
PT (1) PT91317A (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0984136A1 (fr) 1998-09-01 2000-03-08 SCHMID & WEZEL GmbH & Co. Turbine double-face, centrifugale-centripedale
FR2905730A1 (fr) * 2006-09-11 2008-03-14 Jean Andre Bech Procede pour la miniaturisation de turbo-moteurs a combustion
CN100414074C (zh) * 2002-08-26 2008-08-27 张春智 透平膨胀喷射汽轮机
WO2009065416A1 (fr) * 2007-11-20 2009-05-28 Abdelghani Benhama Turbomachine a disques turbines multi etages
ITMI20110684A1 (it) * 2011-04-21 2012-10-22 Exergy Orc S R L Impianto e processo per la produzione di energia tramite ciclo rankine organico
DE102012008710A9 (de) 2012-04-25 2014-01-16 Harald von Hacht Gegenläufige Energiewandler
ITUB20161145A1 (it) * 2016-02-29 2017-08-29 Exergy Spa Metodo per la costruzione di anelli palettati per turbomacchine radiali e anello palettato ottenuto tramite tale metodo

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2515538Y2 (ja) * 1991-12-13 1996-10-30 日本プラスト株式会社 車輌用収納容器の蓋開閉装置
GB2270543B (en) * 1992-09-02 1997-01-15 John Kirby Turbines
GB9218544D0 (en) * 1992-09-02 1992-10-14 Kirby John Turbines
US5443362A (en) * 1994-03-16 1995-08-22 The Hoover Company Air turbine
WO2010107146A1 (fr) * 2009-03-18 2010-09-23 Kim Ki-Tae Turbine du type à réaction
EP2578800A1 (fr) * 2010-05-28 2013-04-10 Teruhiko Ohbo Turbine à vapeur à écoulement radial
US10309232B2 (en) * 2012-02-29 2019-06-04 United Technologies Corporation Gas turbine engine with stage dependent material selection for blades and disk
ITMI20120852A1 (it) * 2012-05-17 2013-11-18 Exergy Orc S R L Sistema orc per la produzione di energia tramite ciclo rankine organico
US10876406B2 (en) 2014-03-21 2020-12-29 Exergy S.P.A. Radial turbomachine
FI127275B (en) * 2015-12-01 2018-02-28 Lappeenrannan Teknillinen Yliopisto Radial turbine impeller and its manufacturing process
ITUA20162126A1 (it) * 2016-03-30 2017-09-30 Exergy Spa Metodo per la costruzione di dischi palettati per turbomacchine radiali e disco palettato ottenuto tramite tale metodo
WO2019123243A1 (fr) * 2017-12-18 2019-06-27 Exergy S.P.A. Procédé, installation et cycle thermodynamique pour la production d'énergie à partir de sources de chaleur à température variable

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US1468694A (en) * 1921-09-19 1923-09-25 Bonom Alfred Flexible and insulating, supporting, and reenforcing rings for crown blades of turbins
US2021078A (en) * 1933-11-08 1935-11-12 Andrew S Miller Turbine
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GB1205632A (en) * 1967-03-28 1970-09-16 William James Lithgow Radial outflow steam turbine
US3726619A (en) * 1971-09-20 1973-04-10 C Adams Rotary fluid-powered apparatus

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Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR373003A (fr) * 1900-01-01
US1468555A (en) * 1921-08-12 1923-09-18 Bonom Alfred Propelling blades for reversible steam turbines
US1468694A (en) * 1921-09-19 1923-09-25 Bonom Alfred Flexible and insulating, supporting, and reenforcing rings for crown blades of turbins
US2021078A (en) * 1933-11-08 1935-11-12 Andrew S Miller Turbine
DE622651C (de) * 1934-04-10 1935-12-03 Siemens Schuckertwerke Akt Ges Dichtung fuer radial beaufschlagte Beschaufelungen von Kreiselmaschinen, insbesondere Dampfturbinen
GB1205632A (en) * 1967-03-28 1970-09-16 William James Lithgow Radial outflow steam turbine
US3726619A (en) * 1971-09-20 1973-04-10 C Adams Rotary fluid-powered apparatus

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0984136A1 (fr) 1998-09-01 2000-03-08 SCHMID & WEZEL GmbH & Co. Turbine double-face, centrifugale-centripedale
CN100414074C (zh) * 2002-08-26 2008-08-27 张春智 透平膨胀喷射汽轮机
FR2905730A1 (fr) * 2006-09-11 2008-03-14 Jean Andre Bech Procede pour la miniaturisation de turbo-moteurs a combustion
WO2009065416A1 (fr) * 2007-11-20 2009-05-28 Abdelghani Benhama Turbomachine a disques turbines multi etages
ITMI20110684A1 (it) * 2011-04-21 2012-10-22 Exergy Orc S R L Impianto e processo per la produzione di energia tramite ciclo rankine organico
WO2012143799A1 (fr) * 2011-04-21 2012-10-26 Exergy Orc S.R.L. Appareil et processus permettant de produire de l'énergie par cycle de rankine organique
EP2743463A3 (fr) * 2011-04-21 2014-09-17 Exergy S.p.A. Appareil et procédé pour la génération d'énergie par cycle de Rankine organique
US9494056B2 (en) 2011-04-21 2016-11-15 Exergy S.P.A. Apparatus and process for generation of energy by organic rankine cycle
DE102012008710A9 (de) 2012-04-25 2014-01-16 Harald von Hacht Gegenläufige Energiewandler
ITUB20161145A1 (it) * 2016-02-29 2017-08-29 Exergy Spa Metodo per la costruzione di anelli palettati per turbomacchine radiali e anello palettato ottenuto tramite tale metodo
WO2017149400A1 (fr) * 2016-02-29 2017-09-08 Exergy S.P.A. Procédé de fabrication d'anneaux à ailettes pour turbomachines et anneau à ailette obtenu grâce audit procédé
US10875132B2 (en) 2016-02-29 2020-12-29 Exergy S.P.A. Method for manufacturing bladed rings for radial turbomachines and bladed ring obtained by this method

Also Published As

Publication number Publication date
GB8818208D0 (en) 1988-09-01
US5071312A (en) 1991-12-10
DK374589D0 (da) 1989-07-28
DK374589A (da) 1990-01-31
JPH0270903A (ja) 1990-03-09
GB2221259A (en) 1990-01-31
PT91317A (pt) 1990-02-08

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